US9188160B2 - Configuration for a roller of a roller bearing - Google Patents

Configuration for a roller of a roller bearing Download PDF

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Publication number
US9188160B2
US9188160B2 US14/119,714 US201214119714A US9188160B2 US 9188160 B2 US9188160 B2 US 9188160B2 US 201214119714 A US201214119714 A US 201214119714A US 9188160 B2 US9188160 B2 US 9188160B2
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Prior art keywords
abutment surface
curvature
starting point
tapered roller
outer end
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US20140126850A1 (en
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Baozhu Liang
Michael Reugels
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SKF AB
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SKF AB
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Assigned to AKTIEBOLAGET SKF reassignment AKTIEBOLAGET SKF ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LIANG, BAOZHU, REUGELS, MICHAEL
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/225—Details of the ribs supporting the end of the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y10T29/49643—Rotary bearing
    • Y10T29/49679—Anti-friction bearing or component thereof
    • Y10T29/49693—Roller making

Definitions

  • the present invention relates to a configuration of a roller of a roller bearing, in particular for a tapered roller bearing.
  • Guide flanges in roller bearings can be either straight or spherical.
  • Straight flanges are mainly used for roller bearings of smaller diameters and thus also smaller flange widths. In this case, a flange width is often too small to produce a defined profile on an available flange surface.
  • Spherical flanges i.e. flanges having a constant curvature, find application mostly in roller bearings having larger diameters and thus also having larger flange widths.
  • a spherical flange is characterized in that a radius, which defines a flange shape facing towards a roller raceway, has its origin substantially on an axis of rotation of the rollers (roller rotational axis), wherein small deviations are allowed due to alignment errors.
  • the sections of the end surfaces of the rollers of conventional bearings which sections oppose the flanges, are spherical, in order to achieve a small contact surface.
  • the curvature of the flange is smaller than the curvature on the end surface of the roller.
  • FIG. 1 shows, in a schematic representation, a longitudinal section of a roller bearing 10 , which is formed in an exemplary manner as a tapered roller bearing.
  • the roller bearing 10 includes a bearing inner ring 11 , a bearing outer ring 12 , and a plurality of rollers 13 , which can roll on races or raceways 14 , 15 formed by the inner sides of the bearing rings 11 , 12 .
  • tapered rollers are the rollers corresponding to the rollers or rolling-element rollers or rolling elements 13 .
  • the tapered rollers 13 can roll on an inner raceway 14 , which is formed in the bearing inner ring 11 , and on an outer raceway 15 , which is formed in the bearing outer ring 12 .
  • the raceways 14 , 15 are formed as conical outer surfaces.
  • the raceways 14 , 15 define, in an imaginary extension, an inner line 16 and an outer line 17 , which meet on an axis of rotation 18 of the roller bearing 10 ideally at a center of rotation 19 .
  • each (tapered) roller 13 rotates around its own roller axis 20 , wherein an imaginary extension of the roller axis 20 ideally also intersects with the center of rotation 19 .
  • a rolling condition on the raceways 14 , 15 is realized by a relative position of the inner line 16 , outer line 17 , bearing axis of rotation 18 , and roller axis 20 , which all intersect in the center of rotation 19 , so that during a relative rotation of bearing inner ring 11 and bearing outer ring 12 , the tapered rollers 13 roll on the raceways 14 , 15 substantially without slippage, and an amount of sliding friction related thereto is minimized.
  • the rollers 13 used in roller bearings can have a curvature on their end side 21 , identified by a radius R, so that the sections of the end side surface of the roller 13 , which sections oppose the flanges, have the shape of a ball surface. As is indicated in the enlargement of FIG. 1 , this surface is in contact at a contact point 22 with a straight- or spherically-embodied flange 23 , for example of the bearing inner ring 11 .
  • the end side 21 can also be flat or have another shape, while the sections of the end surfaces of the roller 13 , which sections oppose the flanges, have a constant curvature.
  • Curvature is generally understood to mean the change in direction per traversed length of an infinitesimally short curved piece.
  • a circle having the radius r thus has the same, constant curvature 1/r everywhere; its direction changes everywhere equally strongly. With all other curves the curvature can vary from curve point to curve point, or along a path on the one three-dimensional surface.
  • the inverse of the curvature is referred to as the radius of curvature. This is the radius of that circle (circle of curvature) which represents the best approximation of the observed curve in the vicinity of the contact point.
  • roller bearings such as for example cylindrical roller-, barrel roller-, or ball-bearings, which are designed with straight or flat flanges
  • the roller-flange contact has a higher surface pressure (Hertzian pressure) between the roller end side 21 and the flange surface.
  • Hertzian pressure is understood to be the greatest pressure that prevails in the middle of the contact surface of two elastic bodies. If, such as with roller bearings having straight flanges, two elastic bodies (curved roller end side and straight or flat flange) are pressed against each other, then in the ideal case they touch only in a punctiform manner.
  • Tapered roller bearings in the large bearing field can, as shown with reference to FIG. 1 , be embodied with spherical flanges 23 , which compared to straight or flat flanges results in a lower surface pressure between the roller end side 21 and the flange surface or abutment surface facing towards the roller 13 .
  • spherically-designed flanges 23 lead, compared to straight flanges, to larger contact ellipses between the roller end side 21 and the opposing flange surface, so that overlappings of the contact ellipse with the flange edges and thus edge stresses can frequently result.
  • One aspect of the present invention is therefore to reduce this sensitivity of the contact point between roller end side and flange with regard to alignment error.
  • an appropriately optimized geometry or configuration of the end surface of the roller is proposed herein, in particular a specific geometry or configuration of an abutment surface for contacting a flange of a bearing ring, with which the rollers having the abutment surface can come into contact.
  • the end surface has an abutment surface for contacting a flange of a bearing ring, the curvature of which abutment surface increases monotonically from a starting point on the abutment surface up to an end of the abutment surface.
  • a low Hertzian pressure is on the one hand ensured by the curved surface, while the risk of an overlapping of the rolling element with the flange edge can simultaneously be minimized by the increase of the curvature up to the end of the abutment surface. That is, the contact point between end surface of the roller and flange is less sensitive to alignment errors.
  • “abutment surface” on the end surface of the roller is understood to be the part of the end surface with which the end surface of the roller can theoretically come into contact with a flange of a bearing ring according the given geometric conditions.
  • the end surface can have additional end surface portions, the geometry of which can be arbitrary, for example flat or curved.
  • a roller for a roller bearing thus has an end surface terminating (located at one end of) the rolling surface of the roller, which end surface has an abutment surface for contacting a flange of a bearing ring, the curvature of which abutment surface increases monotonically from a starting point on the abutment surface up to an end of the abutment surface.
  • the starting point is disposed on the radially outer end of the abutment surface, which radially outer end is adjacent to the raceway and the rolling surface. This can bring about a maximum compensation of skewing in one direction.
  • the starting point is disposed between a radially outer end of the abutment surface, which radially outer end is adjacent to the raceway and the rolling surface, and a radially inner end of the abutment surface, which radially inner end is facing away from the raceway (i.e., is spaced radially inward of the rolling surface), wherein the curvature of the abutment surface increases monotonically from the starting point towards both ends of the abutment surface. In this way a skewing of the bearing can be compensated in two different directions.
  • the roller-flange geometry can be designed such that for an ideal geometry the contact point or contact region between abutment surface and flange lies at the starting point.
  • the curvature increases strongly monotonically from the starting point up to the respective end of the abutment surface, which can ensure an optimal contact ellipse for each point on the abutment surface.
  • the monotonic curvature is such that within a first region comprising the starting point, the curvature increases monotonically or strongly monotonically, wherein in a second region lying between the first region and the end of the abutment surface, the curvature is constant or 0.
  • the abutment surface can thus for example be flat and have the curvature 0.
  • a first region of the abutment surface comprising the starting point has a constant first curvature which is less than a second curvature of the abutment surface in a second region which is adjacent to the first region.
  • the curvature is constant in the first region, and the curvature is also constant in the second region which is adjacent to the first region and between the first region and the end of the abutment surface, but greater than in the first region.
  • a plurality of regions each having constant curvature can neighbor one another, wherein the curvature of each region lying farther in the direction of the end of the abutment surface is greater than the curvature of the region adjacent in the direction of the starting point.
  • the curvature is chosen such that an angle ( ⁇ ) between a tangential plane at the end of the abutment surface and a second tangential plane on a spherical surface extending from the starting point up to the end of the abutment surface, the spherical surface having a curvature corresponding to the curvature at the starting point, falls in a range from greater than 0° to 30°.
  • this increase of the curvature can sufficiently improve the sensitivity with respect to alignment errors.
  • the roller is a tapered roller of a tapered roller bearing.
  • FIG. 1 shows a schematic longitudinal section through a roller bearing having spherical flanges
  • FIG. 2 shows a schematic longitudinal section through a roller having an end surface according to an exemplary embodiment of the present invention
  • FIG. 3 shows a schematic longitudinal section through a roller having an end surface according to a further exemplary embodiment of the present invention
  • FIG. 4 shows a detail enlargement of a schematic longitudinal section through a roller having an end surface according to a further exemplary embodiment of the present invention.
  • FIG. 5 shows a schematic flow diagram for an exemplary embodiment of a manufacturing process for a roller.
  • FIG. 2 shows a schematic longitudinal section through a rolling-element roller (which may be referred to herein as a “roller” or “rolling element”) according to an exemplary embodiment of the present invention.
  • the roller 13 has a roller end surface 21 , which comprises a curved abutment surface 24 , with which the roller is in contact with the flange 23 , or with which it can come into contact in principle due to the geometric edge conditions.
  • the flange 23 has a purely spherical geometry, i.e. the surface of the flange facing towards the roller has a constant curvature in the radial direction over the entire flange height h.
  • the roller 13 also includes a rolling surface 25 in contact with the raceways 14 , 15 .
  • a curvature of an abutment surface 24 on the end side 21 increases monotonically from a starting point 26 on the abutment surface 24 up to an end 28 of the abutment surface, i.e. it becomes continuously larger up to the end.
  • the starting point 26 is located on the radially outer end of the abutment surface 24 , which radially outer end is adjacent to the rolling surface 25 , so that the curvature R 1 is smaller than the curvature R 2 .
  • a first gap size 30 in the vicinity of the contact point 22 is smaller than a more distant second gap size 32 , which leads to a reduced sensitivity to alignment errors.
  • the end surface of the exemplary embodiment depicted has another end surface portion 34 which is flat; however in further exemplary embodiments it can have any other geometries.
  • the curvature shall be understood in this case to mean a change of direction per unit length.
  • the curvature is positive or zero.
  • the curvature e.g. of a straight line is everywhere equal to zero, since its direction does not change.
  • a circle having a radius r has the same curvature everywhere (namely 1/r), since its direction changes everywhere equally strongly. With all other curves the curvature changes from curve point to curve point.
  • the curvature of a curve at a point thus indicates how strongly the curve deviates, in the immediate vicinity of the point, from a straight line.
  • a measure for the curvature of a curved surface can for example also be the increasing deviation of the surface from a plane tangential to the surface at a given point.
  • a stronger curvature makes itself noticeable as a stronger deviation from the plane.
  • a monotonically increasing curvature thus means that if one moves along a locus curve along a surface, with each infinitesimal step along the locus curve the curvature either is larger or remains the same.
  • a strongly-monotonically-increasing curvature correspondingly means that with each infinitesimal step the curvature along the locus curve is larger.
  • the starting point 26 is located directly on an end of the abutment surface 24 , which end is adjacent to the rolling surface 25 .
  • the curvature thus increases monotonically from the starting point 26 up to the end 28 of the abutment surface 24 , which end 28 is facing away from the raceway, in stated differently, is spaced radially inward from the rolling surface 25 .
  • FIG. 3 schematically shows a further exemplary embodiment wherein the curvature does not increase strongly monotonically but rather in sections. That is, in a first region 36 of the abutment surface 24 , which first region 36 comprises the starting point 26 , this first region 36 has a constant curvature R 1 which is smaller than a second curvature R 2 of the abutment surface in a second region 38 adjacent to the first region.
  • the starting point 26 is disposed between a radially outer end 40 of the abutment surface 24 , which outer end 40 is adjacent to the rolling surface 25 , and a radially inner end 28 of the abutment surface 24 , which inner end is spaced radially inward of the rolling surface 25 , wherein the curvature of the abutment surface increases monotonically or strongly monotonically from the starting point 26 towards both ends of the abutment surface 24 .
  • the change of curvature of the abutment surface 24 can be defined for example by determining the angle ⁇ between a tangential plane 42 at the end 40 or 28 of the abutment surface 24 and a second tangential plane 44 on a spherical surface 46 that extends from the starting point 26 up to the end of the abutment surface 24 , the curvature of which spherical surface 46 corresponds to the curvature at the starting point 26 , as illustrated in FIG. 4 .
  • the monotonically or strongly monotonically increasing curvature of the abutment surface 24 makes possible a change of curvature of the abutment surface 24 in an angular range ⁇ from greater than 0° up to 30°, preferably in a range 0° 0′ 6′′ ⁇ 30°.
  • a roller for a roller bearing having an end surface terminating a raceway is provided.
  • an abutment surface 24 for a flange of a bearing ring is produced on the end surface, the curvature of which abutment surface 24 increases monotonically from a starting point 26 on the abutment surface 24 up to an end 28 of the abutment surface 24 .
  • the proposed rollers are suited to reduce the sensitivity of the roller-flange contact point to alignment errors and skewing of the bearing in use, but nevertheless to be able to ensure a sufficient guiding of the roller on the raceway during operation.
  • Embodiments of the inventive rollers ensure a good roller guiding with low Hertzian pressure, as well as a low risk for edge overlaps and the undesirable edge stresses resulting therefrom.
  • embodiments of the inventive roller geometry may have the following advantageous features:
  • the proposed roller-flange geometry is designed such that the contact point can lie near the starting point between the roller end side and the flange. If the contact point shifts due to alignment errors towards the ends of the abutment surface, then the sensitivity is greatly reduced, which can prevent a “wandering” of the theoretical contact point out over the flange edge and thus can also prevent high edge pressures.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
US14/119,714 2011-05-24 2012-05-24 Configuration for a roller of a roller bearing Active 2032-08-31 US9188160B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102011076329 2011-05-24
DE102011076329.5 2011-05-24
DE102011076329A DE102011076329B4 (de) 2011-05-24 2011-05-24 Geometriekonzept für eine Wälzkörperrolle eines Rollenlagers
PCT/EP2012/059736 WO2012160147A1 (de) 2011-05-24 2012-05-24 Geometriekonzept für eine wälzkörperrolle eines rollenlagers

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US20140126850A1 US20140126850A1 (en) 2014-05-08
US9188160B2 true US9188160B2 (en) 2015-11-17

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US14/119,714 Active 2032-08-31 US9188160B2 (en) 2011-05-24 2012-05-24 Configuration for a roller of a roller bearing

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US (1) US9188160B2 (de)
EP (1) EP2715169B1 (de)
CN (1) CN103906939B (de)
DE (1) DE102011076329B4 (de)
WO (1) WO2012160147A1 (de)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
US20150300410A1 (en) * 2014-04-16 2015-10-22 Jtekt Corporation Bearing ring for roller bearing, roller bearing, and power transmission device
US20220333640A1 (en) * 2019-09-19 2022-10-20 Ntn Corporation Tapered roller bearing
US20220373030A1 (en) * 2019-09-19 2022-11-24 Ntn Corporation Tapered roller bearing

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CN103032469B (zh) * 2012-12-14 2015-09-09 瓦房店轴承集团有限责任公司 球基面曲率变异圆锥滚子
JP2015113972A (ja) * 2013-12-16 2015-06-22 株式会社ジェイテクト 円すいころ軸受及び動力伝達装置
JP6350099B2 (ja) * 2014-08-11 2018-07-04 株式会社ジェイテクト 円すいころ軸受
WO2017020906A1 (de) * 2015-08-04 2017-02-09 Schaeffler Technologies AG & Co. KG Verfahren und vorrichtung zur herstellung eines schrägrollenlagers
US10816034B2 (en) * 2017-02-20 2020-10-27 Ntn Corporation Tapered roller bearing
DE102017129773A1 (de) * 2017-12-13 2019-06-13 Schaeffler Technologies AG & Co. KG Pendelrollenlager
DE102020211036B4 (de) * 2020-09-02 2022-04-14 Aktiebolaget Skf Anordnung mit einem Schleifwerkzeug und einer Rolle für ein Rollenlager sowie Verfahren zum Herstellen einer Rolle für ein Rollenlager

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US4915513A (en) * 1987-05-22 1990-04-10 Glaenzer Spicer Crossed tapered roller bearing and application thereof in a hub for an automobile
JPH04331813A (ja) 1991-04-30 1992-11-19 Ntn Corp 円すいころ軸受
DE102005061179A1 (de) 2005-12-21 2007-06-28 Schaeffler Kg Wälzlager und Verfahren zu dessen Herstellung
US20090003747A1 (en) 2005-12-21 2009-01-01 Schaeffler Kg Rolling Bearing
DE102008020068A1 (de) 2008-04-22 2009-10-29 Schaeffler Kg Wälzlager mit gekrümmten Kontaktflächen

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JP2000065066A (ja) * 1998-08-19 2000-03-03 Nippon Seiko Kk 円筒ころ軸受
JP3731401B2 (ja) * 1999-08-31 2006-01-05 日本精工株式会社 ころ軸受
DE102004039845B4 (de) * 2004-08-18 2013-04-11 Schaeffler Technologies AG & Co. KG Axial-Kegelrollenlager
JP2006316837A (ja) * 2005-05-11 2006-11-24 Ntn Corp 円錐ころ軸受および鉄道車両車軸支持構造
JP2007051702A (ja) * 2005-08-18 2007-03-01 Jtekt Corp 円錐ころ軸受、及びこれを用いた車両用ピニオン軸支持装置

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Publication number Priority date Publication date Assignee Title
US1736037A (en) * 1927-06-04 1929-11-19 Timken Roller Bearing Co Roller bearing
US4915513A (en) * 1987-05-22 1990-04-10 Glaenzer Spicer Crossed tapered roller bearing and application thereof in a hub for an automobile
JPH04331813A (ja) 1991-04-30 1992-11-19 Ntn Corp 円すいころ軸受
DE102005061179A1 (de) 2005-12-21 2007-06-28 Schaeffler Kg Wälzlager und Verfahren zu dessen Herstellung
US20080292233A1 (en) 2005-12-21 2008-11-27 Schaeffler Kg Rolling Bearing and Method for the Production Thereof
US20090003747A1 (en) 2005-12-21 2009-01-01 Schaeffler Kg Rolling Bearing
DE102008020068A1 (de) 2008-04-22 2009-10-29 Schaeffler Kg Wälzlager mit gekrümmten Kontaktflächen

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150300410A1 (en) * 2014-04-16 2015-10-22 Jtekt Corporation Bearing ring for roller bearing, roller bearing, and power transmission device
US10161452B2 (en) * 2014-04-16 2018-12-25 Jtekt Corporation Bearing ring for roller bearing, roller bearing, and power transmission device
US20220333640A1 (en) * 2019-09-19 2022-10-20 Ntn Corporation Tapered roller bearing
US20220373030A1 (en) * 2019-09-19 2022-11-24 Ntn Corporation Tapered roller bearing
US11746825B2 (en) * 2019-09-19 2023-09-05 Ntn Corporation Tapered roller bearing
US11754121B2 (en) * 2019-09-19 2023-09-12 Ntn Corporation Tapered roller bearing

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DE102011076329B4 (de) 2013-11-21
DE102011076329A1 (de) 2012-11-29
CN103906939A (zh) 2014-07-02
US20140126850A1 (en) 2014-05-08
EP2715169B1 (de) 2017-09-20
EP2715169A1 (de) 2014-04-09
CN103906939B (zh) 2017-02-15
WO2012160147A1 (de) 2012-11-29

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